CN110873050B

CN110873050B - Compression mechanism, compressor, refrigeration cycle device and air conditioner

Info

Publication number: CN110873050B
Application number: CN201811006105.2A
Authority: CN
Inventors: 郑礼成; 吴延平
Original assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2018-08-30
Filing date: 2018-08-30
Publication date: 2024-11-01
Anticipated expiration: 2038-08-30
Also published as: CN110873050A

Abstract

The invention provides a compression mechanism, a compressor, a refrigeration cycle device and an air conditioner, wherein the compression mechanism comprises: the cylinder is provided with a sliding vane groove, a mounting groove and a threaded hole in sequence from the central axis of the cylinder to the outer side wall of the cylinder, wherein the sliding vane groove is communicated with the mounting groove, and the threaded hole is communicated with the mounting groove; the valve plate is arranged in the mounting groove; the threaded fastener is connected with the threaded hole in a matched mode and applies extrusion force to the valve plate; the distance from the central axis of the threaded fastener to any axial section of the sliding vane groove is gradually increased from one end of the sliding vane groove, which is close to the central axis of the cylinder, to one end of the sliding vane groove, which is far away from the central axis of the cylinder. According to the compression mechanism disclosed by the invention, the acting force of the screw fastener on the valve plate is decomposed into two acting forces perpendicular to the direction of the valve plate and parallel to the direction of the valve plate, the deformation generated by the two acting forces is mutually counteracted, and the final comprehensive effect greatly reduces the deformation of the sliding vane groove, so that the reliability of the compressor is effectively improved.

Description

Compression mechanism, compressor, refrigeration cycle device and air conditioner

Technical Field

The present invention relates to the field of refrigeration equipment, and more particularly, to a compression mechanism, a compressor, a refrigeration cycle apparatus, and an air conditioner.

Background

In winter, because the indoor and outdoor temperature difference is large, the heating capacity of the air conditioning system in a low-temperature environment is greatly attenuated, and the heat demand of a user cannot be met. The reasons are as follows: firstly, in a low-temperature environment, the density of the refrigerant at the air suction port of the compressor is smaller, so that the suction quantity of the refrigerant is reduced, and the heating quantity of an air conditioning system is influenced; secondly, because the indoor and outdoor temperature difference is large, the evaporation temperature and the condensation temperature of the air conditioning system are greatly different, a large amount of gas can be flashed after throttling, so that the refrigerant distribution among different flow paths of the evaporator is uneven, the heat exchange efficiency of the evaporator is affected, and meanwhile, because the flash gas enters the evaporator to absorb smaller heat, the flash gas occupies a large pipeline space of the evaporator, the large surface area of the pipeline loses the function of liquid conduction, and the heat exchange efficiency of the evaporator is further affected.

In order to solve the problem, in the related art, a gas refrigerant injection method is applied to a compressor and a refrigeration cycle, and a double-cylinder rotary compressor is used. However, the cost of the compressor is obviously increased by adopting the double-cylinder compressor to carry out injection technology, and if the energy efficiency or heating capacity is not obviously improved, the cost performance is low; the other mode is to provide an independent compression structure, and to add an independent sliding vane compression cavity, namely a second working cavity, to suck the gas with intermediate pressure from the second working cavity, so that on one hand, a part of expansion work can be recovered, on the other hand, the dryness of the low-pressure refrigerant entering the evaporator is reduced, and the heat exchange efficiency of the evaporator is improved, but the valve plate of the current independent compression structure is usually fixed by a jackscrew, and the deformation of a sliding vane groove can be frequently caused after the jackscrew is tightened, so that the problem of the sliding vane blocking is caused, and the reliability of the compressor is seriously influenced.

Disclosure of Invention

The present invention aims to solve at least one of the technical problems existing in the prior art or related art.

To this end, a first aspect of the invention proposes a compression mechanism.

A second aspect of the present invention proposes a compressor.

A third aspect of the present invention proposes a refrigeration cycle apparatus.

A second aspect of the present invention proposes an air conditioner.

In view of this, a first aspect of the present invention provides a compression mechanism comprising: the cylinder is provided with a sliding vane groove, a mounting groove and a threaded hole in sequence from the central axis of the cylinder to the outer side wall of the cylinder, wherein the sliding vane groove is communicated with the mounting groove, and the threaded hole is communicated with the mounting groove; the valve plate is arranged in the mounting groove; the threaded fastener is connected with the threaded hole in a matched mode and applies extrusion force to the valve plate; the distance from the central axis of the threaded fastener to any axial section of the sliding vane groove is gradually increased from one end of the sliding vane groove, which is close to the central axis of the cylinder, to one end of the sliding vane groove, which is far away from the central axis of the cylinder.

According to the compression mechanism, the distance from the central axis of the threaded fastener to any axial section of the sliding vane groove is gradually increased from one end of the sliding vane groove close to the central axis of the cylinder to one end of the sliding vane groove far away from the central axis of the cylinder, namely, the direction from the inner end of the sliding vane groove on one side of the center of the cylinder to the outer end of the sliding vane groove is gradually increased, so that the acting force of the screw fastener on the valve plate is decomposed into two acting forces perpendicular to the direction of the valve plate, the acting force perpendicular to the direction of the valve plate fastens the valve plate on the mounting end surface of the mounting groove, the sliding vane groove is deformed in the narrowing direction, the acting force parallel to the direction of the valve plate causes the valve plate to generate reaction force on the cylinder, the sliding vane groove is deformed in the widening direction, the deformation generated by the two acting forces are mutually offset, and the final comprehensive effect causes the deformation of the sliding vane groove to be greatly reduced, and the reliability of the compressor is effectively improved.

In addition, the compression mechanism in the technical scheme provided by the invention can also have the following additional technical characteristics:

In the above technical solution, preferably, the included angle between the central axis of the threaded fastener and any axial section of the slide groove has a value range of 15 ° or more and 60 ° or less.

In the technical scheme, the deformation fluctuation of the sliding vane groove can be reduced by setting the value range of the included angle between the central axis of the threaded fastener and any axial section of the sliding vane groove between 15 degrees and 60 degrees, so that the operation reliability of the compressor is ensured.

In any of the above technical solutions, preferably, the number of the threaded holes is an even number, and the threaded holes are uniformly distributed on two sides of the sliding vane groove.

In this technical scheme, set up the screw hole in gleitbretter groove both sides to guarantee the sealing of the installation terminal surface of mounting groove, usually set up 2 or 4 screw holes. When the 4 threaded holes are formed, the positions of the threaded holes correspond to the four corner areas of the valve plate respectively, and the sealing reliability is good due to the large number of threaded fasteners; when setting up 2 screw holes, its position along cylinder chamber axis direction is located the valve plate middle part, because threaded fastener quantity is less relatively, can adopt great diameter and great tightening torque.

In any of the above technical solutions, preferably, a ratio between a distance between two screw holes opposite to each other at both sides of the slide groove and close to the slide groove and a width of the mounting groove in a radial direction of the cylinder is 0.5 or more.

In the technical scheme, the position of the threaded hole has larger influence on the deformation of the sliding vane groove, the closer the threaded hole of the air cylinder is to the center of the sliding vane groove, the farther the equivalent acting force of the threaded fastener on the mounting end face of the mounting groove is from the side face of the mounting groove, namely the larger the acting force arm of the acting force is, the larger the deformation of the generated sliding vane groove is, the narrower the sliding vane groove is, the ratio between the distance S between the two threaded holes positioned on the two sides of the sliding vane groove and the width L of the mounting groove is increased, the deformation of the sliding vane groove is reduced, and when S/L is more than or equal to 0.5, the deformation change is relatively slow.

In any of the above aspects, preferably, the compression mechanism further includes: the groove is arranged on the cylinder and is positioned at the matching position of the valve plate and the threaded fastener; the groove is tapered along the radial cross-sectional shape of the cylinder.

In the technical scheme, the threaded fastener contact part is provided with a groove with a conical cross section, and the conical groove can be only positioned at the part contacted with the threaded fastener and can also penetrate through the valve plate along the central axis direction of the cylinder cavity. Due to the conical grooves, the problem that acting force perpendicular to the sliding vane groove direction is limited by friction coefficient is solved. Therefore, through optimizing the included angle theta between the central axis of the threaded fastener and the axial interface of the sliding vane groove, the deformation of the sliding vane groove caused by the assembly of the threaded fastener is greatly improved.

The cross-sectional shape of the groove along the radial direction of the cylinder may be square, circular, or any other cross-sectional shape formed by a straight line or an arc line, and the like, which can achieve the same purpose, and should not be taken as a limitation of the present invention.

In any of the above-described aspects, preferably, a chamfer plane is formed on an outer side face of the valve plate facing the mounting groove side, and the threaded fastener is engaged with the chamfer plane to apply a pressing force to the valve plate.

In any of the above aspects, preferably, the chamfer plane is perpendicular to the axis of the threaded fastener.

In the technical scheme, the contact position of the threaded fastener is arranged on the chamfer plane formed by the edges of the two sides of the sliding vane groove on the outer side face of the valve plate, and the chamfer plane is perpendicular to the axis of the threaded fastener, so that the pretightening force of the threaded fastener is ensured to be always along the axis direction of the threaded fastener.

In any of the above aspects, preferably, the compression mechanism further includes: the sliding vane is slidably arranged in the sliding vane groove, and a second working cavity is formed between the sliding vane and the valve plate in the sliding vane groove.

In any of the above aspects, preferably, the compression mechanism further includes:

The roller is arranged in a cylinder cavity of the cylinder in a rolling way, one end of the sliding sheet is connected with the roller, and a first working cavity is formed among the inner peripheral surface of the cylinder cavity, the outer peripheral surface of the roller and the sliding sheet.

In the technical scheme, the sliding vane can slide inside and outside the sliding vane groove, the roller is sleeved on the eccentric part of the crankshaft and can eccentrically rotate along with the rotation of the crankshaft, in addition, the roller can also rotate around the axis of the roller, and the inner end of the sliding vane is propped against the roller. The inner peripheral surface of the cylinder cavity, the outer peripheral surface of the roller and the sliding sheets are formed into a first working cavity, and the upper end surface and the lower end surface of the first working cavity are sealed by an upper bearing and a lower bearing. The part of the first working cavity connected with the first air suction hole is a first air suction cavity, and the part connected with the first air discharge hole is a first compression cavity. With the rotation of the crankshaft, the volume of the first air suction cavity is continuously increased, so that the refrigerant is continuously sucked, the volume of the first compression cavity is continuously reduced, the pressure of the refrigerant in the cavity is continuously increased, the first air discharge valve plate is pushed open when the pressure reaches the air discharge pressure, the high-pressure refrigerant is discharged from the first air outlet, and the lift of the first air discharge valve plate is limited by the first limiter, so that the reliability problems such as fracture and the like are prevented.

The sliding vane groove is positioned between the sliding vane and the valve plate to form a second working cavity, and the upper end surface and the lower end surface of the second working cavity are sealed by an upper bearing and a lower bearing. The inner end of the sliding vane is connected with the roller in a hinged mode, so that the sliding vane is prevented from being separated under any condition, and the sliding vane linearly reciprocates in the sliding vane groove along with the rotation of the crankshaft. When the sliding vane moves inwards (towards the axis of the cylinder cavity), the volume of the second working cavity is increased, the suction valve plate is opened to a certain extent, and the refrigerant with intermediate pressure (the pressure is higher than the suction pressure of the first working cavity) is sucked; when the sliding vane moves outwards (away from the axis of the cylinder cavity), the volume of the second working cavity is reduced, the refrigerant is compressed, the pressure is continuously increased, the second exhaust valve plate is pushed open when the exhaust pressure is reached, the high-pressure refrigerant is discharged from the second exhaust port, and similarly, the second limiter limits the lift of the second exhaust valve plate. Through adopting two working chamber structures, promote the work efficiency of compressor to promote the user and experience the use of air conditioner.

A second aspect of the present invention provides a compressor comprising a compression mechanism as claimed in any one of the preceding claims.

The compressor provided by the invention comprises the compression mechanism in any technical scheme, so that the compressor has all beneficial effects of the compression mechanism and is not repeated herein.

A third aspect of the present invention provides a refrigeration cycle apparatus comprising: a compression mechanism according to any one of the above aspects; or the compressor according to the above technical scheme.

The refrigeration cycle device provided by the invention comprises the compression mechanism or the compressor of any one of the technical schemes, so that the refrigeration cycle device has all the beneficial effects of the compression mechanism and the compressor, and the description is omitted.

A third aspect of the present invention provides an air conditioner, comprising: the refrigeration cycle apparatus according to the above-described aspect.

The air conditioner provided by the invention comprises the refrigeration cycle device of the technical scheme, so that the air conditioner has all the beneficial effects of the refrigeration cycle device and is not repeated herein.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 is a schematic view of a working chamber and valve plate securing structure of a prior art independent compression structure;

FIG. 2 is a cross-sectional elevation view of a prior art stand-alone compression structure;

FIG. 3 is a schematic illustration of the deformation principle of a sliding vane groove of a prior valve plate fixing structure;

FIG. 4 is a schematic diagram of a compression mechanism according to one embodiment of the invention;

FIG. 5 is an illustration of the compression mechanism improvement principle of the embodiment of FIG. 4;

FIG. 6 is a graph showing deformation of the slide groove and an included angle θ;

FIG. 7 is a schematic diagram of a profile of slide slot deformation versus cylinder threaded hole distance S/cylinder mounting slot width L;

FIG. 8 is a schematic view of a compression mechanism according to yet another embodiment of the present invention;

Fig. 9 is a schematic structural view of a compression mechanism according to still another embodiment of the present invention;

Fig. 10 is a schematic view of a structure of a refrigeration cycle apparatus according to an embodiment of the present invention.

Wherein, the correspondence between the reference numerals and the component names in fig. 1 to 3 is:

The device comprises a cylinder 1', a crankshaft 2', a roller 3', a sliding vane 4', a sliding vane groove 42', an upper bearing 5', a lower bearing 6', a threaded hole 7', a mounting groove 8', a valve plate 82', a suction valve plate 9', a second working cavity 10', a first suction hole 11', a first exhaust hole 12', a second limiter 14', a second exhaust valve plate 15', a second exhaust hole 16 and a jackscrew 17 '.

The correspondence between the reference numerals and the component names in fig. 4 to 10 is:

1 cylinder, 12 slide groove, 122 slide, 14 mounting groove, 142 valve plate, 144 suction valve plate, 146 groove, 148 chamfer plane, 16 screw hole, 162 screw fastener, 18 first suction hole, 10 first working chamber, 20 second working chamber, 30 compressor, 40 four-way valve, 50 outdoor heat exchanger, 60 first throttling element, 70 flash evaporator, 80 second throttling element, 90 indoor heat exchanger.

Detailed Description

In order that the above-recited objects, features and advantages of the present application will be more clearly understood, a more particular description of the application will be rendered by reference to the appended drawings and appended detailed description. It should be noted that, without conflict, the embodiments of the present application and features in the embodiments may be combined with each other.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, but the present invention may be practiced in other ways than those described herein, and therefore the scope of the present invention is not limited to the specific embodiments disclosed below.

A compression mechanism, a compressor, a refrigeration cycle apparatus, and an air conditioner according to some embodiments of the present invention are described below with reference to fig. 4 to 10.

As shown in fig. 4 to 9, one embodiment of the present invention provides a compression mechanism including: the air cylinder 1, there are slip sheet groove 12, mounting groove 14 and threaded hole 16 sequentially from central axis of the air cylinder 1 to outside wall of the air cylinder 1 on the air cylinder 1, the slip sheet groove 12 communicates with mounting groove 14, the threaded hole 16 communicates with mounting groove 14; a valve plate 142 disposed in the mounting groove 14; a threaded fastener 162, the threaded fastener 162 being cooperatively connected with the threaded hole 16 and exerting a pressing force on the valve plate 142; the distance from the central axis of the threaded hole 16 of the threaded fastener 162 to any axial section of the sliding vane groove 12 gradually increases from one end of the sliding vane groove 12 close to the central axis of the cylinder 1 to one end of the sliding vane groove 12 far away from the central axis of the cylinder 1.

According to the compression mechanism of the invention, the distance from the central axis of the threaded hole 16 of the threaded fastener 162 to any axial section of the sliding vane groove 12 is set to be gradually increased from one end of the sliding vane groove 12 close to the central axis of the cylinder 1 to one end of the sliding vane groove 12 far away from the central axis of the cylinder 1, namely, the direction from the inner end of the sliding vane groove 12 on one side of the center of the cylinder 1 to the outer end is gradually increased, so that the acting force of the threaded fastener on the valve plate 142 is decomposed into two acting forces in the directions perpendicular to the valve plate 142, the acting force in the direction perpendicular to the valve plate 142 fastens the valve plate 142 on the mounting end surface of the mounting groove 14, the sliding vane groove 12 is deformed in the narrowing direction, the acting force in the direction parallel to the valve plate 142 causes the valve plate 142 to generate reactive force on the cylinder 1, the sliding vane groove 12 is deformed in the widening direction, the deformation generated by the two acting forces are mutually offset, and the final comprehensive effect causes the deformation of the sliding vane groove 12 to be greatly reduced, and the reliability of the compressor is effectively improved.

In some embodiments of the present invention, the threaded fastener 162 employs a jackscrew.

In the related art, as shown in fig. 1 to 3, a compressor pump body of a conventional independent compression structure includes: the cylinder 1', the crankshaft 2', the roller 3', the slide 4', the upper bearing 5', the lower bearing 6', the first discharge valve plate, the first stopper (the first discharge valve plate and the first stopper are not shown in the drawing and are located on the upper bearing 5' or the lower bearing 6 '), the valve plate 82', the suction valve plate 9', the second discharge valve plate 15', the second stopper 14' and the jackscrew 17'. The cylinder 1' is provided with a cylindrical cylinder 1' cavity, a first air suction hole 11', a first exhaust hole 12', a sliding vane groove 42', a mounting groove 8' and a threaded hole 7', wherein the mounting groove 8' is arranged at the outer end of the sliding vane groove 42' and is communicated with the sliding vane groove 42', the surface of a communication port of the mounting groove 8' connected with the sliding vane groove 42' forms a mounting end face, and the threaded hole 7' is arranged at the outer end of the mounting groove 8' and is communicated with the mounting groove 8 '. Here, the cylindrical cylinder 1' has an axis, the inner end of the vane groove 42' means the end of the vane groove 42' facing the axis, and the outer end of the vane groove 42' means the end of the vane groove 42' facing away from the axis.

The sliding vane 4' can slide inside and outside the sliding vane groove 42', the roller 3' is sleeved on the eccentric part of the crankshaft 2' and can eccentrically rotate along with the rotation of the crankshaft 2', in addition, the roller 3' can also rotate around the axis of the roller 3', and the inner end of the sliding vane 4' is propped against the roller 3 '. The first working chamber is formed among the inner peripheral surface of the chamber of the cylinder 1', the outer peripheral surface of the roller 3' and the sliding vane 4', and the upper end surface and the lower end surface of the first working chamber are sealed by an upper bearing 5' and a lower bearing 6 '. The part of the first working chamber connected with the first suction hole 11 'is a first suction chamber, and the part connected with the first discharge hole 12' is a first compression chamber. With the rotation of the crankshaft 2', the volume of the first suction cavity is continuously increased, so that the refrigerant is continuously sucked, the volume of the first compression cavity is continuously reduced, the pressure of the refrigerant in the cavity is continuously increased, the first exhaust valve plate is pushed open when the exhaust pressure is reached, the high-pressure refrigerant is discharged from the first exhaust hole 12', and the lift of the first exhaust valve plate is limited by the first limiter, so that the reliability problems such as fracture and the like are prevented.

The second working chamber 10 'is formed in the vane groove 42' between the vane 4 'and the valve plate 82', and its upper and lower end surfaces are sealed by the upper bearing 5 'and the lower bearing 6'. The inner end of the sliding vane 4 'is connected with the roller 3' in a hinged mode, so that the sliding vane 4 'and the roller are not separated under any condition, and the sliding vane 4' linearly reciprocates in the sliding vane groove 42 'along with the rotation of the crankshaft 2'. When the sliding vane 4 'moves inwards (towards the cavity axis of the air cylinder 1'), the volume of the second working cavity 10 'is increased, the suction valve plate 9' is opened to a certain extent, and the refrigerant with intermediate pressure (the pressure is higher than the suction pressure of the first working cavity) is sucked; when the slide sheet 4' moves outwards (away from the cavity axis of the cylinder 1 '), the volume of the second working cavity 10' is reduced, the refrigerant is compressed, the pressure is continuously increased, the second exhaust valve plate 15' is pushed away when the exhaust pressure is reached, the high-pressure refrigerant is discharged from the second exhaust hole 16', and similarly, the second limiter 14' limits the lift of the second exhaust valve plate 15 '.

The valve plate 82', the suction valve plate 9' are matched with the mounting end surface of the mounting groove 8' of the cylinder 1', and in order to ensure sealing, a jackscrew 17' is usually adopted for pre-tightening, namely, the jackscrew 17' is mounted in a threaded hole 7' at the outer end of the mounting groove 8' of the cylinder 1', as shown in fig. 1 and 3, the axis of the jackscrew 17' is parallel to the sliding vane groove 42', and the valve plate 82' and the suction valve plate 9' are pressed on the mounting end surface. The jackscrew 17 'structure has advantages such as simple structure, simple to operate, pretightning force are adjustable, therefore become the first choice of installation terminal surface sealing means, but this structure compressor often appears gleitbretter groove 42' and warp big problem that leads to gleitbretter 4 'to block after jackscrew 17' pretightning, has seriously influenced the reliability of compressor, becomes the bottleneck problem of this structure application.

In view of this problem, as shown in fig. 4, the distance from the central axis of the threaded fastener 162 to any axial section of the vane groove 12 in the compression mechanism according to the present invention increases gradually from the end of the vane groove 12 near the central axis of the cylinder 1 to the end of the vane groove 12 far from the central axis of the cylinder 1. When the threaded fasteners 162 are disposed on both sides of the sliding vane groove 12, the distance between the central axis of at least one threaded fastener 162 and the sliding vane groove 12 increases gradually from the inner end of the sliding vane groove 12 to the outer end of any axial section of the sliding vane groove 12.

As shown in fig. 3 and 5, it can be seen that the compressing mechanism provided by the present invention can effectively improve the deformation problem of the assembling slide groove 12. The specific comparison is as follows:

as shown in fig. 3, under the existing structural design of the jackscrew 17', the axis of the jackscrew 17' is parallel to the sliding vane groove 42', after the jackscrew 17' is tightened, the jackscrew 17' generates a larger pretightening force, and the mounting end surface of the mounting groove 8' of the air cylinder 1' is correspondingly acted by the pressing force transmitted by the valve plate 82' and the air suction valve plate 9 '. The reaction force of the valve plate 82' to the jackscrew 17' is applied to the whole formed by the cylinder 1' and the jackscrew 17', and the reaction force is the same as the pretightening force of the jackscrew 17 '; at the same time, the mounting end surface of the mounting groove 8 'of the cylinder 1' is also acted by the pressing force transmitted by the valve plate 82 'and the suction valve plate 9', and the pressing force is actually a distribution force, and the equivalent resultant force of the distribution force is shown in the figure. The equivalent resultant force of the reaction force of the valve plate 82 'to the jackscrew 17' and the pressing force transmitted by the suction valve plate 9 'is parallel to the slide groove 42'. Due to the arrangement of the mounting groove 8 'of the air cylinder 1', the local rigidity of the sliding vane groove 42 'is seriously weakened, and the sliding vane groove 42' of the air cylinder 1 'is obviously deformed mainly under the action of the pressing force transmitted by the air suction valve plate 9', and the deformed shape is shown by a dotted line in fig. 4, namely, the outer end of the sliding vane groove 42 'is obviously narrowed, and the inner end of the sliding vane groove 42' is slightly widened, so that the shape is verified in a theoretical and experimental mode. The width of the narrowing of the slide groove 42 'exceeds the width gap between the slide groove 42' and the slide 4', resulting in the locking of the slide 4'.

When the vane groove 42' is greatly deformed, the fluctuation of the deformation is also usually large due to the fluctuation of various manufacturing factors in mass production, which means that if the width gap between the vane 4' and the vane groove 42' is simply increased, the actual width gap between the vane 4' and the vane groove 42' after assembly of part of the compressor is excessively large, so that the leakage through the width gap is obviously increased when the compressor is operated, and the performance is obviously deteriorated; meanwhile, the inclination of the sliding vane 4 'is increased (a small included angle is formed between the sliding vane 4' and the sliding vane groove 42 '), so that the side surface of the sliding vane 4' is abnormally worn, and the reliability of the compressor is affected. Therefore, deformation of the slide groove 42' due to the assembly must be reduced.

As shown in fig. 5, according to the compression mechanism provided by the invention, the distance between the central axis of the threaded fastener 162 and any axial section of the sliding vane groove 12 is gradually increased from the inner end of the sliding vane groove 12 to the outer end, and at this time, the whole body of the threaded fastener 162 and the cylinder 1 is subjected to a force F parallel to the sliding vane groove 12, and the pretightening force of the threaded fastener 162 is not perpendicular to the contact surface of the valve plate 142, but also generates a force F parallel to the surface of the valve plate 142, i.e. perpendicular to the sliding vane groove 12. The resultant of forces F and F is the reaction of the pretension of threaded fastener 162. The deformation of the slide groove 12 caused by the force F parallel to the slide groove 12 is similar to that of fig. 3, but the slide groove 12 as a whole will also have a widening deformation effect under the action of the force F perpendicular to the slide groove 12, the deformation direction of which is opposite to that of the force F, and the deformations cancel each other. Under the combined action of the two, the deformation of the sliding vane groove 12 is obviously reduced, and the deformed shape is shown as a broken line in fig. 5, wherein the outer end of the sliding vane groove 12 is slightly narrowed, and the inner end of the sliding vane groove is slightly widened. In one embodiment of the invention, the deformation of the slide groove 12 caused by the pre-tightening of the jackscrew is reduced from 12.5 μm of the original design to 1.7 μm of the improved design of the invention, and the improvement amplitude of the slide groove 12 reaches 86.4%.

In one embodiment of the present invention, the included angle between the central axis of the threaded bore 16 of the threaded fastener 162 and any axial cross-section of the slide slot 12 is preferably in the range of 15 ° or more and 60 ° or less.

In this embodiment, by setting the range of the included angle between the central axis of the threaded hole 16 of the threaded fastener 162 and any one of the axial sections of the vane groove 12 to 15 ° to 60 °, the fluctuation of the deformation of the vane groove 12 can be reduced to ensure the reliability of the operation of the compressor.

In an embodiment, as shown in fig. 6, the included angle between the central axis of the threaded fastener 162 and any axial section of the sliding vane groove 12 has a great influence on the improvement effect of the deformation of the sliding vane groove 12. The positive values of deformation shown in fig. 6 indicate that the slide groove 12 is narrowed, the negative values indicate that the slide groove 12 is widened, i.e., the positive and negative signs indicate the deformation direction, and the numerical values indicate the deformation magnitude. This curve is obtained with the force F in the direction parallel to the slide groove 12 kept constant, taking into account the sealing requirements of the mounting end face of the mounting groove 14 of the cylinder 1. Meanwhile, as can be seen from fig. 5, f=f×tan θ, as the included angle θ increases, the acting force F gradually increases, and the curve in fig. 6 assumes that the increase of the acting force F is not limited by other factors, i.e. the pretightening force of the threaded fastener 162 is always along the axial direction thereof. When the included angle theta is smaller than 45 degrees, after the threaded fastener 162 is pre-tightened, the acting force F parallel to the direction of the sliding vane groove 12 is larger, the acting force F acts more obviously, the sliding vane groove 12 is narrowed, and the deformation of the sliding vane groove 12 is rapidly reduced along with the increase of the included angle theta; in contrast, when the included angle θ is greater than 45 degrees, the acting force f perpendicular to the direction of the slide groove 12 is greater after the screw fastener 162 is pre-tightened, and the acting force f acts more significantly, so that the slide groove 12 appears to be widened, and as the included angle θ increases, the acting force f increases rapidly, resulting in rapid deterioration of the deformation of the slide groove 12. As described above, too large deformation (whether widening or narrowing) of the slide groove 12 causes large fluctuation in the deformation in mass production, so that smaller deformation of the slide groove 12 is preferable. As can be seen from fig. 6, the included angle θ is preferably set between 15 ° and 60 °.

In one embodiment of the present invention, the number of threaded holes 16 is preferably an even number, evenly distributed on both sides of the slider groove 12.

In this embodiment, screw holes 16 are provided on both sides of the slide groove 12, so that sealing of the mounting end face of the mounting groove 14 is ensured, and usually 2 or 4 screw holes 16 are provided. When the 4 threaded holes 16 are formed, the positions of the threaded holes correspond to the four corner areas of the valve plate 142 respectively, and the sealing reliability is good due to the large number of the threaded fasteners 162; when 2 screw holes 16 are provided, the positions thereof in the axial direction of the cylinder chamber are located in the middle of the valve plate 142, and a larger diameter and a larger tightening torque can be used because of the relatively small number of screw fasteners 162.

In one embodiment of the present invention, it is preferable that a ratio between a distance between two screw holes 16 located at both sides of the vane groove 12 and close to the opposite side of the vane groove 12 and a width of the mounting groove 14 in a radial direction of the cylinder 1 is 0.5 or more.

In this embodiment, the position of the threaded hole 16 has a larger influence on the deformation of the slide groove 12, and the closer the threaded hole 16 of the cylinder 1 is to the center of the slide groove 12, the farther the equivalent acting force of the threaded fastener 162 to the mounting end surface of the mounting groove 14 is from the side surface of the mounting groove 14, that is, the larger the acting force arm of the acting force is, the larger the generated deformation of the slide groove 12 is, which is shown as the slide groove 12 becomes narrower, as shown in fig. 7, as the ratio between the distance S between the two threaded holes 16 located at both sides of the slide groove 12 and the width L of the mounting groove 14 increases, the deformation of the slide groove 12 decreases, and when S/L is equal to or greater than 0.5, the deformation change is relatively slow.

In an embodiment, as shown in fig. 4, the threaded fastener 162 is a jackscrew that may be disposed entirely within the threaded bore 16 of the cylinder 1, thereby avoiding interference problems. The valve plate 142 contacted with the front end of the jackscrew is a plane, so that the acting force f parallel to the surface of the valve plate 142 is completely provided by friction force, the contact area between the front end of the jackscrew and the valve plate 142 is small, and a certain deformation can be locally generated, so that the local static friction coefficient mu is favorably increased. The maximum value of the static friction force F is entirely dependent on the static friction coefficient when the force F parallel to the slide groove 12 is unchanged: as can be seen from fig. 5, f=f=tan θ, so μ=tan θ, θ=arctan μ is obtained. The coefficient of friction μ is typically between 0.3 and 0.4 in this embodiment, so that the static friction force f will not increase any more when the angle θ is greater than arctan μ, i.e., 17 ° to 22 °. Thereafter, if the angle θ is further increased, the jack screw pretension will deviate from its axis. As can be seen from fig. 6, the improvement of the deformation of the vane groove 12 is limited due to the limitation of the static friction force f, and the deformation of the vane groove 12 still becomes narrow. It should be noted that, the jackscrew is a relatively convenient design as one of the threaded fasteners 162, but some changes made on this basis, such as changing the jackscrew to another screw, and the connection form is not changed essentially, should not be regarded as circumventing the present patent.

In one embodiment of the present invention, preferably, the compression mechanism further includes: a groove 146, which is arranged on the cylinder 1 and is positioned at the matching position of the valve plate 142 and the threaded fastener 162; the groove 146 is tapered in the radial cross-sectional shape of the cylinder 1.

In this embodiment, as shown in fig. 8, the contact portion of the threaded fastener 162 is provided with a groove 146 having a tapered cross-sectional shape, and the tapered groove 146 may be located only at a portion in contact with the threaded fastener 162 or may extend through the valve plate 142 in the cylinder chamber central axis direction. Due to the tapered recess 146, the problem of friction coefficient limitation of forces perpendicular to the slide slot 12 is solved. Thereby greatly improving the deformation of the vane groove 12 caused by the assembly of the threaded fastener 162 by optimizing the included angle theta between the central axis of the threaded fastener 162 and the axial interface of the vane groove 12.

It should be noted that the cross-sectional shape of the recess 146 along the radial direction of the cylinder 1 may be square, circular, or any other cross-sectional shape formed by a straight line or an arc line, etc. to achieve the same purpose, and should not be taken as a limitation of the present invention.

In one embodiment of the present invention, the outer side of the valve plate 142 facing the side of the mounting groove 14 is preferably formed with a chamfer surface 148, and the threaded fastener 162 cooperates with the chamfer surface 148 to apply a pressing force to the valve plate 142.

In one embodiment of the invention, the chamfer surface 148 is preferably perpendicular to the axis of the threaded fastener 162.

In this embodiment, as shown in fig. 9, the contact position of the threaded fastener 162 is set on the chamfer plane 148 formed by the outer side surface of the valve plate 142 at the edges of both sides of the sliding vane groove 12, and the chamfer plane 148 is perpendicular to the axis of the threaded fastener 162, so as to ensure that the pretightening force of the threaded fastener 162 is always along the axis direction thereof. In one embodiment of the present invention, preferably, the compression mechanism further includes: the sliding vane 122, the sliding vane 122 is slidably disposed in the sliding vane groove 12, and the second working chamber 20 is formed in the sliding vane groove 12 between the sliding vane 122 and the valve plate 142.

In one embodiment of the present invention, preferably, the compression mechanism further includes:

The roller is rollably provided in a cylinder chamber of the cylinder 1, one end of the vane 122 is connected to the roller, and a first working chamber 10 is formed between an inner peripheral surface of the cylinder chamber, an outer peripheral surface of the roller, and the vane 122.

In this embodiment, the slide 122 can slide inside and outside the slide groove 12, the roller is sleeved on the eccentric part of the crankshaft and can eccentrically rotate along with the rotation of the crankshaft, in addition, the roller can rotate around the axis of the roller, and the inner end of the slide 122 is abutted against the roller. The first working chamber 10 is formed between the inner peripheral surface of the cylinder chamber, the outer peripheral surface of the roller, and the slide 122, and the upper and lower end surfaces thereof are sealed by an upper bearing and a lower bearing. The portion of the first working chamber 10 connected to the first suction hole 18 is a first suction chamber, and the portion connected to the first discharge hole is a first compression chamber. With the rotation of the crankshaft, the volume of the first air suction cavity is continuously increased, so that the refrigerant is continuously sucked, the volume of the first compression cavity is continuously reduced, the pressure of the refrigerant in the cavity is continuously increased, the first air discharge valve plate is pushed open when the pressure reaches the air discharge pressure, the high-pressure refrigerant is discharged from the first air outlet, and the lift of the first air discharge valve plate is limited by the first limiter, so that the reliability problems such as fracture and the like are prevented.

The second working chamber 20 is formed in the vane groove 12 between the vane 122 and the valve plate 142, and its upper and lower end surfaces are sealed by upper and lower bearings. The inner ends of the sliding sheets 122 are connected with the rollers in a hinged mode, so that the sliding sheets 122 are prevented from being separated in any situation, and the sliding sheets 122 do linear reciprocating motion in the sliding sheet grooves 12 along with rotation of the crankshaft. When the slide 122 moves inwards (towards the axis of the cylinder cavity), the volume of the second working cavity 20 increases, the suction valve plate 144 is opened to a certain extent, and the refrigerant with intermediate pressure (the pressure is higher than the suction pressure of the first working cavity 10) is sucked in; when the slide 122 moves outwards (away from the axis of the cylinder cavity), the volume of the second working chamber 20 is reduced, the refrigerant is compressed, the pressure is continuously increased, the second exhaust valve plate is pushed open when the exhaust pressure is reached, the high-pressure refrigerant is discharged from the second exhaust port, and similarly, the second limiter limits the lift of the second exhaust valve plate. Through adopting two working chamber structures, promote the work efficiency of compressor to promote the user and experience the use of air conditioner.

A further embodiment of the invention provides a compressor comprising a compression mechanism as in any of the embodiments above.

The compressor provided by the invention comprises the compression mechanism in any embodiment, so that the compressor has all the beneficial effects of the compression mechanism and is not repeated herein.

Yet another embodiment of the present invention provides a refrigeration cycle apparatus including: the compression mechanism of any one of the embodiments described above; or a compressor as in the above embodiment.

The refrigeration cycle device provided by the invention comprises the compression mechanism of any embodiment or the compressor of the embodiment, so that the refrigeration cycle device has all the beneficial effects of the compression mechanism and the compressor, and the description is omitted.

In a specific embodiment, as shown in fig. 10, the refrigeration cycle apparatus includes: a compressor 30, a four-way valve 40, an outdoor heat exchanger 50, a first throttling element 60, a flash evaporator 70, a second throttling element 80, and an indoor heat exchanger 90. The four-way valve 40 is in a refrigerating mode when the refrigerating device is in the state of the figure, the high-pressure refrigerant compressed by the first working chamber 10 and the second working chamber 20 is mixed in the compressor 30 (can also be mixed outside the compressor 30 and is not considered as limiting the refrigerating device of the invention), flows to the outdoor heat exchanger 50 together for condensation, the condensed liquid refrigerant is throttled to the required intermediate pressure by the throttling element, then is separated in the flash evaporator 70, and the separated saturated liquid refrigerant enters the throttling element again for throttling, finally reaches the evaporating pressure value and enters the indoor heat exchanger 90 for evaporation. The evaporated refrigerant returns to the first working chamber 10 again through the first suction hole 18 for compression. And the intermediate pressure gas separated in the flash evaporator 70 is returned to the second working chamber 20 through the second suction hole for compression.

Normally, work done by the expansion of the refrigerant throttle in the refrigeration cycle device is completely wasted, while the intermediate pressure gas separated by the flash evaporator 70 in the refrigeration cycle device of the present invention is directly returned to the second working chamber 20 for compression, which is equivalent to recovering a part of expansion work. In addition, the saturated liquid refrigerant enters the indoor heat exchanger 90, that is, the dryness of the refrigerant in the indoor heat exchanger 90 is reduced, so that the heat exchange efficiency of the indoor heat exchanger 90 is improved.

The refrigeration cycle device can be switched to a heating mode through the four-way valve 40, and high-pressure refrigerant compressed by the first working chamber 10 and the second working chamber 20 flows to the indoor heat exchanger 90 together for condensation, the condensed liquid refrigerant is throttled to a required intermediate pressure through the throttling element, then is separated in the flash evaporator 70, and the separated saturated liquid refrigerant enters the throttling element again for throttling, and finally reaches an evaporation pressure value to enter the outdoor heat exchanger 50 for evaporation. The evaporated refrigerant returns to the first working chamber 10 again through the first suction hole 18 for compression. And the intermediate pressure gas separated in the flash evaporator 70 is returned to the second working chamber 20 through the second suction hole for compression.

Under the condition of large indoor and outdoor temperature difference, the heating capacity of the air conditioning system is greatly improved in a low-temperature environment, and the requirement of a user on the heating capacity can be effectively met.

It will be appreciated that the compression mechanism of the present invention may be used with single cylinder compressors as well as multi-cylinder compressors.

Still another aspect of the present invention provides an air conditioner, including: the refrigeration cycle apparatus of the above embodiment.

The air conditioner provided by the invention comprises the refrigeration cycle device of the embodiment, so that the air conditioner has all the beneficial effects of the refrigeration cycle device and is not repeated herein.

In addition, in the description of the present invention, the terms "center", "length", "width", "thickness", "upper", "lower", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element in question must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more. The terms "coupled," "mounted," "secured," and the like are to be construed broadly, and may be fixedly coupled, detachably coupled, or integrally connected, for example; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.

In the description of the present invention, the terms "one embodiment," "some embodiments," "particular embodiments," and the like, mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In the present invention, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A compression mechanism, comprising:

The cylinder is provided with a sliding vane groove, a mounting groove and a threaded hole in sequence from the central axis of the cylinder to the outer side wall of the cylinder, the sliding vane groove is communicated with the mounting groove, and the threaded hole is communicated with the mounting groove;

The valve plate is arranged in the mounting groove;

The air suction valve plate is matched with the valve plate;

The second exhaust valve plate is matched with the valve plate;

the threaded fastener is connected with the threaded hole in a matching way and applies extrusion force to the valve plate;

The distance from any point of the threaded fastener on the central axis of the threaded fastener to the axis of the sliding vane groove gradually increases from one end of the sliding vane groove, which is close to the central axis of the cylinder, to one end of the sliding vane groove, which is far away from the central axis of the cylinder.

2. The compression mechanism of claim 1, wherein the compression mechanism is configured to compress the compressed air,

The included angle between the central axis of the threaded fastener and the axis of the sliding vane groove is 15 degrees or more and 60 degrees or less.

3. The compression mechanism of claim 1, wherein the compression mechanism is configured to compress the compressed air,

The number of the threaded holes is even, and the threaded holes are uniformly distributed on two sides of the sliding sheet groove.

4. A compression mechanism according to claim 3, wherein,

The ratio of the distance between the two opposite threaded holes which are positioned on two sides of the sliding vane groove and close to the sliding vane groove and the width of the mounting groove along the radial direction of the air cylinder is more than or equal to 0.5.

5. The compression mechanism of any one of claims 1 to 4, further comprising: the groove is arranged on the cylinder and is positioned at the matching position of the valve plate and the threaded fastener;

The groove is tapered along the radial cross-sectional shape of the cylinder.

6. The compression mechanism according to any one of claim 1 to 4, wherein,

The outer side surface of the valve plate facing the mounting groove side is provided with a chamfer plane, and the threaded fastener is matched with the chamfer plane so as to apply extrusion force to the valve plate.

7. The compression mechanism of claim 6, wherein the compression mechanism is configured to compress the compressed air,

The chamfer plane is perpendicular to an axis of the threaded fastener.

8. The compression mechanism of any one of claims 1 to 4, further comprising: and the sliding vane is slidably arranged in the sliding vane groove, and a second working cavity is formed between the sliding vane and the valve plate in the sliding vane groove.

9. The compression mechanism of any one of claims 1 to 4, further comprising:

The roller is arranged in the cylinder cavity of the cylinder in a rolling way, one end of the sliding vane is connected with the roller, and a first working cavity is formed among the inner peripheral surface of the cylinder cavity, the outer peripheral surface of the roller and the sliding vane.

10. A compressor comprising a compression mechanism as claimed in any one of claims 1 to 9.

11. A refrigeration cycle apparatus, comprising:

a compression mechanism as claimed in any one of claims 1 to 9; or (b)

The compressor of claim 10.

12. An air conditioner, comprising: the refrigeration cycle apparatus of claim 11.